US5110267A - Positive-displacement pump for pumping alimentary liquids - Google Patents

Positive-displacement pump for pumping alimentary liquids Download PDF

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Publication number
US5110267A
US5110267A US07/446,768 US44676889A US5110267A US 5110267 A US5110267 A US 5110267A US 44676889 A US44676889 A US 44676889A US 5110267 A US5110267 A US 5110267A
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United States
Prior art keywords
piston
cylinder
stem
actuating
ball valve
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Expired - Fee Related
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US07/446,768
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English (en)
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Alberto Giordani
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1002—Ball valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/108—Valves characterised by the material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • F04B9/113—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting liquid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/02—Rubber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

Definitions

  • the present invention relates to a reciprocating positive displacement pump particularly suitable for the pumping of oenological liquids such as wines, musts, distillates, vinegars and the like, of alimentary oils and of other alimentary liquids and/or beverages such as fruit juices and pulps, sugary juices, etc.
  • oenological liquids such as wines, musts, distillates, vinegars and the like
  • alimentary oils and of other alimentary liquids and/or beverages such as fruit juices and pulps, sugary juices, etc.
  • the food industry employs single- or two-cylinder positive-displacement piston pumps, the actuation stem of which is reciprocatingly actuated by a connecting-rod/crank system.
  • the positive displacement pumps used are normally of the single- or two-cylinder kind with distribution provided by ball valves made of rubber with metallic central cores. In these cases the length of the stroke of the piston is equal to the diameter of the circle traced by the small end of the connecting rod.
  • the actuation system in fact provides a liquid flow which is pulsating rather than constant due to the fact that the speed of the piston (and therefore of the liquid) varies for each stroke of the piston from a zero value when the piston is at one end of the cylinder to a maximum value at mid-stroke and then back to the zero value at the end of the stroke.
  • the change in the flow-rate of the liquid and therefore in the speed thereof entails considerable turbulence of the liquid which results in high stresses on the delivery pipes and a water hammer effect, as well as possible wear and/or breakage of the pipes.
  • the disadvantage is worsened by the fact that in oenological plants the pipes are normally made of flexible material and are generally not coupled to fixed supports.
  • the liquid flow-rate is dependent on the maximum length of the piston's stroke which, in practice, is defined by the diameter of the circle defined by the connecting rod's small end, which depends on the diameter of the flywheel used to actuate the piston's system.
  • the aim of the present invention is to overcome the above described disadvantages by providing the oenological industry and the industry of alimentary liquids in general, including dense liquids, with a two-stage positive displacement pump structured and actuated so as to create pumping with increased and constant flow rates without increasing the diameter of the pump's piston, and with a smaller number of piston stroke reversals and therefore a smaller number of speed changes with respect to what is provided by the known art, so as to advantageously result in less vibration.
  • An object of the invention is to provide a pump of the above specified type which is dimensioned so as to allow much higher pump filling coefficients than those obtainable with known positive-displacement pumps and to allow a reduced wear of the inflow and delivery ball valves, thus significantly reducing the noise produced by the system.
  • a further object of the invention is to provide a positive displacement pump which allows the flow rate to be varied in a simple and rapid manner, without varying the piston's speed, and for which scoring or damage of the internal walls of the pump's cylinder is prevented even when solid foreign matter is present between the cylinder walls and the piston's sealing gaskets.
  • Another object is to provide a pump which can be used and installed in any environmental condition, including immersion in a liquid.
  • a further object is to provide a decanting pump for the above specified applications which is structured and dimensioned so that it can be easily installed, together with the piston actuation devices, on a towable or self-propelled trolley to facilitate its movement.
  • FIG. 1 is a schematic view of a two-stage positive displacement pump according to the invention
  • FIG. 2 is a sectional view of a seat for a sealing valve, made of elastically resilient material, such as rubber or the like, and with a metallic core, to reduce the noise produced by the pump and extend the useful life of the seat;
  • FIG. 3 is a time diagram of the variations of the speed of the piston of a reciprocating double-action pump, actuated by means of known connecting-rod/crank systems;
  • FIG. 4 is the time diagram of the variations of the speed of the piston of a reciprocating double-action pump according to the invention.
  • a decanting pump P comprises a hydraulic cylinder 1 made of stainless steel, inside which a piston 2 sealingly slides and is peripherally provided with an appropriate gasket 3.
  • the piston 2 has a stem 4 which extends through a front wall 1a and is sealingly slidable therethrough.
  • the hydraulic cylinder 1 is fluidically connected into a fluid network. Specifically, the hydraulic cylinder 1 is connected, at its opposite ends, to two longitudinal ducts 5, 5a through passages 6 in which conventional ball valves 7, 7a and 8, 8a made of rubber surrounding metallic cores are arranged.
  • the valves 7, 7a constitute inlet valves which are operable to allow fluid to flow from the longitudinal inlet duct 5 into the passage 6.
  • the valves 8, 8a constitute delivery valves which are operable to allow fluid to flow from the passages 6 into the longitudinal outlet duct 5a.
  • the longitudinal inlet duct 5 is connected, by means of a tube 9, to the container of the liquid to be decanted, whereas the longitudinal outlet duct 5a is connected to a tube 10 for delivering the pumped liquid to a decanting container.
  • the stem 4 of the pump's piston 2 is coaxially and rigidly connected with the stem 4a of another piston 11 which is mounted sealingly and slidably within a hydraulic cylinder 12 and is reciprocable in both directions by pressurized fluid, such as oil, which is alternately fed through ports 13, 13a, by a conventional hydraulic control unit 14.
  • the control unit 14 is provided with an oil tank and with a related conventional oil-air or oil-water heat exchanger.
  • the pressurized oil is fed to the control unit 14 by a variable flow rate positive displacement pump 15 actuated by an electric motor 16 (or by an internal-combustion engine).
  • the alternating reversal of the flow of pressurized oil in the hydraulic cylinder 12 is performed by the control unit 14 upon an actuation imparted by a cam-like element 17 or the like which is rigidly connected to the stem 4, such that as the stem 4 is reciprocated, the cam 17 is moved back and forth and alternately makes contact with two limit switches 18, 18a.
  • the limit switches 18, 18a are constituted by position sensors associated with hydraulic, electric or other known shunting valves which, upon every impact with the cam 17, transmit a signal to the control unit 14, which reverses the hydraulic flow to the cylinder 12.
  • the alternated reversal of the pump's piston can be provided by means of a distributing valve which can deflect the flow in the hydraulic cylinder 12 every time a maximum preset pressure is reached in the pump.
  • a distributing valve which can deflect the flow in the hydraulic cylinder 12 every time a maximum preset pressure is reached in the pump.
  • the assembly formed by the positive displacement pump 1, the hydraulic cylinder 12, the associated limit switches 18, 18a, the control unit 14 and the positive displacement pump 15 with associated motor 16 can be easily mounted on a towable or self-propelled trailer in order to facilitate its movement among various areas of utilization.
  • valve seats 19 are made of rubber with a metal core 20 and are provided with holes 21 for fixing them, by means of screws or the like 22, to the body of the pump P.
  • the operation of the above described two-stage positive displacement pump is conventional. That is, it operates as a double-action pump with intake and discharge cycles performed by the piston 2 which, during a leftward stroke (as viewed in FIG. 1), sucks the liquid in through the inlet valve 7, while the opposite inlet valve 7a remains pressed in its seat so that the liquid present in the portion of the cylinder 1 to the left (as viewed in FIG. 1) of the piston 2 is compressed and forced through the delivery valve 8a to the longitudinal delivery duct 5a.
  • the reverse (rightward) stroke the liquid is sucked in through the inlet valve 7a while the inlet valve 7 is forced to remain closed such that the liquid contained in the part of the cylinder 1 to the right (as viewed in FIG. 1) of the piston 2 is compressed and forced through the delivery valve 8 and into the longitudinal delivery duct 5a.
  • the piston 2 reciprocates in the hydraulic cylinder 1 with an equal stroke length in both directions such that the sliding of the piston 2 is as constant as possible and, therefore, incurs very short direction reversal times.
  • the reversal of the direction of the piston movement is also facilitated by the small masses which are in motion and by the absence of a flywheel and of the associated prior art connecting-rod systems.
  • the adoption of a hydraulic cylinder results in highly precise pumping cycles and speed even when the speed of the motor fluctuates or when the temperature of the oil of the hydraulic circuit varies.
  • the hydraulic cylinder of the decanting pump P can furthermore be made longer, for example 2.5 times longer or more, than the cylinder of current pumps actuated by crank systems. In this manner, a greater intake capacity and therefore a greater volumetric efficiency are achieved.
  • the number of stroke reversals of the piston 2 is smaller than for known pumps having equal flow-rates. Therefore, the ball valves 7, 7a and 8, 8a are worked less than in conventional systems and have a longer useful life.
  • variation of the flow rate of the decanting pump P according to the invention is achieved by varying the number of cycles thereof, which is, of course, achieved by varying the flow rate of the hydraulic pump 15 of the hydraulic circuit. This can be accomplished by means of an adapted external regulator which can be positioned even remotely from the variable flow rate hydraulic pump 15.
  • a plurality of such regulators can be mounted in batteries, with no limitations in number, in order to control the flow rate in a programmable manner.
  • the solution according to the present invention offers the advantage of providing a number of cycles which is normally between 30-35 per minute as opposed to a number of cycles equal to 70-75 per minute normally adopted in known decanting pumps.
  • the variation of the piston's speed over time as illustrated by the diagram of FIG. 3, furthermore entails pulsating flow which can vary from zero to a maximum value and back to zero, between which there are extensive regions 23 with no flow rate which must be compensated for in order to attempt to even out the flow as much as possible.
  • the variation of the piston's movement speed over time as illustrated in FIG. 4, entails pumping actions with a substantially constant flow rate, with only small regions 24 to be compensated for.
  • Another advantage of the present invention is that it allows flow rate variations by varying only the stroke of the piston 2, rather than its speed, by moving the limit switches 18, 18a.
  • a further feature of the invention is that the two mutually rigidly associated stems 4, 4a and the respective pistons 2 and 11 can be rotated about their common axis by having the cam 17 in contact with a rotating shaft 25 provided with axial grooves 26, such that when the shaft 25 rotates, the cam 17 and thus the stems 4, 4a and pistons 2, 11 are also rotated. With this arrangement, a slight rotation can be imparted to the stems 4, 4a and the pistons 2, 11 for every stroke of the pistons 2, 1. Such rotation of the pistons 2, 11 is effective to prevent the formation of longitudinal scores on the surface of the cylinder, thus uniformly distributing its wear.
  • the central hydraulic distribution unit can be further provided with a device which reverses the flow when the actuation fluid reaches a "preset" maximum operating pressure of the hydraulic pump.
  • a device which reverses the flow when the actuation fluid reaches a "preset" maximum operating pressure of the hydraulic pump.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US07/446,768 1988-12-06 1989-12-06 Positive-displacement pump for pumping alimentary liquids Expired - Fee Related US5110267A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT22869A/88 1988-12-06
IT8822869A IT1227502B (it) 1988-12-06 1988-12-06 Pompa volumetrica per il pompaggio di liquidi alimentari in genere e, in particolare, per impieghi in campo enologico

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US5110267A true US5110267A (en) 1992-05-05

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US07/446,768 Expired - Fee Related US5110267A (en) 1988-12-06 1989-12-06 Positive-displacement pump for pumping alimentary liquids

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US (1) US5110267A (it)
EP (1) EP0380777B1 (it)
DE (1) DE68913186T2 (it)
IT (1) IT1227502B (it)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5302090A (en) * 1991-12-05 1994-04-12 Schoo Raul A I Method and apparatus for the utilization of the energy stored in a gas pipeline
US5411374A (en) * 1993-03-30 1995-05-02 Process Systems International, Inc. Cryogenic fluid pump system and method of pumping cryogenic fluid
US5564912A (en) * 1995-09-25 1996-10-15 Peck; William E. Water driven pump
US5768972A (en) * 1995-01-19 1998-06-23 Mcneilus Truck And Manufacturing, Inc. Air logic system for side loader
US6357235B1 (en) * 2000-03-02 2002-03-19 Cacumen Ltda. Power generation system and method
US20090321475A1 (en) * 2008-06-27 2009-12-31 Schultz Carl L Dispensing and metering system
WO2010066069A1 (zh) * 2008-12-12 2010-06-17 Yu Chun Kwan 流体动力装置
WO2013177268A1 (en) * 2012-05-22 2013-11-28 Charles David Mccoy Gas compressor
US20140199182A1 (en) * 2013-01-11 2014-07-17 Super Products Llc Reciprocating water pump
US20140322035A1 (en) * 2013-03-15 2014-10-30 Richard F. McNichol Drive system for surface hydraulic accumulator
CN105952607A (zh) * 2016-05-19 2016-09-21 四川理工学院 一种液压驱动的大流量计量泵
US20170184090A1 (en) * 2013-01-11 2017-06-29 Super Products Llc Reciprocating water pump
JP2017210961A (ja) * 2016-05-26 2017-11-30 マン ディーゼル アンド ターボ フィリアル ア マン ディーゼル アンド ターボ エスイー チュスクランＭＡＮ Ｄｉｅｓｅｌ ＆ Ｔｕｒｂｏ，ｆｉｌｉａｌ ａｆ ＭＡＮ Ｄｉｅｓｅｌ ＆ Ｔｕｒｂｏ ＳＥ，Ｔｙｓｋｌａｎｄ 大型２ストローク圧縮点火高圧ガス噴射内燃エンジンのための燃料供給システム

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PT8668U (pt) * 1992-12-09 1996-01-31 Briel Electrodomesticos Valvula de escoamento de efeito duplo para maquinas de cafe
ES2134703B1 (es) * 1996-10-15 2000-04-16 Garcia Juan Rafael Muela Dispositivo para el trasvase del orujo del aceite.
FR2829146B1 (fr) * 2001-08-31 2004-10-01 Jean Louis Bouillet Dispositif de remontage de jus et/ou de transfert de la vendange
EP1783368A1 (en) * 2005-11-07 2007-05-09 Dresser Wayne Aktiebolag Vapour recovery pump
IT1393374B1 (it) * 2008-09-11 2012-04-20 Lancellotti Apparecchio per travasare aceto balsamico tradizionale ad alta densita'
CN111594413B (zh) * 2020-05-11 2021-11-23 合肥通用机械研究院有限公司 一种远距离机械动力驱动的往复式潜液液氢泵

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US1173326A (en) * 1915-02-18 1916-02-29 Angie L Benner Air-operated tool.
US3099016A (en) * 1960-08-11 1963-07-30 Edwards Miles Lowell Heart valve
US3234746A (en) * 1964-04-28 1966-02-15 Olin Mathieson Process and apparatus for the transfer of liquid carbon dioxide
DE1550530A1 (de) * 1966-07-29 1969-10-09 Schlecht Dipl Ing Karl Kugelventil fuer Dickstoffpumpen
US3628638A (en) * 1970-02-02 1971-12-21 Us Army Hydraulic mitigator
US3700359A (en) * 1971-05-18 1972-10-24 Science Inc Explosion-proof liquid fuel pump
US3775028A (en) * 1971-10-12 1973-11-27 C Davis Pump unit for water supply
US3901129A (en) * 1972-05-01 1975-08-26 Butterworth Hydraulic Dev Ltd Fluid pressure operated reciprocating motors
US4209285A (en) * 1977-11-09 1980-06-24 The Richardson Company Unitary pump packing

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GB217170A (en) * 1923-06-08 1924-10-30 Arie Van Wingerden Improvements in or relating to non-return valves for suction pumps
FR2525288B1 (fr) * 1982-04-19 1988-09-16 Unima Anjou Dispositif de commande d'une pompe alternative, en particulier pour pulverisateur a usage agricole
US4666374A (en) * 1983-01-11 1987-05-19 Cooper Industries, Inc. Methods and apparatus for producing uniform discharge and suction flow rates
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1173326A (en) * 1915-02-18 1916-02-29 Angie L Benner Air-operated tool.
US3099016A (en) * 1960-08-11 1963-07-30 Edwards Miles Lowell Heart valve
US3234746A (en) * 1964-04-28 1966-02-15 Olin Mathieson Process and apparatus for the transfer of liquid carbon dioxide
DE1550530A1 (de) * 1966-07-29 1969-10-09 Schlecht Dipl Ing Karl Kugelventil fuer Dickstoffpumpen
US3628638A (en) * 1970-02-02 1971-12-21 Us Army Hydraulic mitigator
US3700359A (en) * 1971-05-18 1972-10-24 Science Inc Explosion-proof liquid fuel pump
US3775028A (en) * 1971-10-12 1973-11-27 C Davis Pump unit for water supply
US3901129A (en) * 1972-05-01 1975-08-26 Butterworth Hydraulic Dev Ltd Fluid pressure operated reciprocating motors
US4209285A (en) * 1977-11-09 1980-06-24 The Richardson Company Unitary pump packing

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5302090A (en) * 1991-12-05 1994-04-12 Schoo Raul A I Method and apparatus for the utilization of the energy stored in a gas pipeline
US5411374A (en) * 1993-03-30 1995-05-02 Process Systems International, Inc. Cryogenic fluid pump system and method of pumping cryogenic fluid
US5477690A (en) * 1993-03-30 1995-12-26 Process Systems International, Inc. Liquid cryogenic storage tank system
US5551488A (en) * 1993-03-30 1996-09-03 Process System International, Inc. Method of filling a two-compartments storage tank with cryogenic fluid
US5768972A (en) * 1995-01-19 1998-06-23 Mcneilus Truck And Manufacturing, Inc. Air logic system for side loader
US5564912A (en) * 1995-09-25 1996-10-15 Peck; William E. Water driven pump
US6357235B1 (en) * 2000-03-02 2002-03-19 Cacumen Ltda. Power generation system and method
US20090321475A1 (en) * 2008-06-27 2009-12-31 Schultz Carl L Dispensing and metering system
US8511513B2 (en) * 2008-06-27 2013-08-20 Nordson Corporation Dispensing and metering system
WO2010066069A1 (zh) * 2008-12-12 2010-06-17 Yu Chun Kwan 流体动力装置
WO2013177268A1 (en) * 2012-05-22 2013-11-28 Charles David Mccoy Gas compressor
US10443590B1 (en) * 2012-05-22 2019-10-15 Charles David McCoy Gas compressor compressing well head casing gas
US20140199182A1 (en) * 2013-01-11 2014-07-17 Super Products Llc Reciprocating water pump
US20170184090A1 (en) * 2013-01-11 2017-06-29 Super Products Llc Reciprocating water pump
US20140322035A1 (en) * 2013-03-15 2014-10-30 Richard F. McNichol Drive system for surface hydraulic accumulator
CN105952607A (zh) * 2016-05-19 2016-09-21 四川理工学院 一种液压驱动的大流量计量泵
JP2017210961A (ja) * 2016-05-26 2017-11-30 マン ディーゼル アンド ターボ フィリアル ア マン ディーゼル アンド ターボ エスイー チュスクランＭＡＮ Ｄｉｅｓｅｌ ＆ Ｔｕｒｂｏ，ｆｉｌｉａｌ ａｆ ＭＡＮ Ｄｉｅｓｅｌ ＆ Ｔｕｒｂｏ ＳＥ，Ｔｙｓｋｌａｎｄ 大型２ストローク圧縮点火高圧ガス噴射内燃エンジンのための燃料供給システム
KR20170134213A (ko) * 2016-05-26 2017-12-06 맨 디젤 앤드 터보 필리얼 아프 맨 디젤 앤드 터보 에스이 티스크랜드 대형 2 행정 압축 점화 고압 가스 분사 내연기관용 연료 공급 시스템
JP2018162790A (ja) * 2016-05-26 2018-10-18 マン ディーゼル アンド ターボ フィリアル ア マン ディーゼル アンド ターボ エスイー チュスクランＭＡＮ Ｄｉｅｓｅｌ ＆ Ｔｕｒｂｏ，ｆｉｌｉａｌ ａｆ ＭＡＮ Ｄｉｅｓｅｌ ＆ Ｔｕｒｂｏ ＳＥ，Ｔｙｓｋｌａｎｄ 大型２ストローク圧縮点火高圧ガス噴射内燃エンジンのための燃料供給システム
KR102056061B1 (ko) 2016-05-26 2020-01-22 만 에너지 솔루션즈, 필리알 아프 만 에너지 솔루션즈 에스이, 티스크란드 대형 2 행정 압축 점화 고압 가스 분사 내연기관용 연료 공급 시스템
JP2023030027A (ja) * 2016-05-26 2023-03-07 マン エナジー ソリューションズ フィリアル ア マン エナジー ソリューションズ エスイー チュスクラン 大型２ストローク圧縮点火高圧ガス噴射内燃エンジンのための燃料供給システム

Also Published As

Publication number Publication date
DE68913186T2 (de) 1994-10-06
IT8822869A0 (it) 1988-12-06
DE68913186D1 (de) 1994-03-24
EP0380777B1 (en) 1994-02-16
EP0380777A1 (en) 1990-08-08
IT1227502B (it) 1991-04-12

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